Oil supply device

ABSTRACT

An oil supply device that includes a first pump configured to discharge oil by being driven by power transferred along the power transfer path; a second pump configured to discharge the oil by being driven by a power source independent of the power transfer path; a first supply oil passage through which the oil discharged from the first pump is supplied to the transmission; and a second supply oil passage through which the oil discharged from the second pump is supplied to the friction engagement device.

BACKGROUND

The present disclosure relates to an oil supply device.

In vehicular drive transmission device, for example, oil is generallyused for controlling an engagement state of a friction engagement deviceand lubricating an intermesh portion between gears in a transmission. Anoil supply device is provided in order to supply the oil to each portionof the vehicular drive transmission device. Japanese Patent ApplicationPublication No. 2015-197146 (JP 2015-197146 A) discloses an example ofthe oil supply device.

The oil supply device of JP 2015-197146 A supplies oil to each portionof a vehicular drive transmission device [vehicular drive device]including a friction engagement device [clutch KO] and a transmission[transmission 33] in order from an internal combustion engine [internalcombustion engine 2] side in a power transfer path connecting theinternal combustion engine to wheels. The oil supply device mainlyincludes a first pump [mechanical oil pump 34] to be driven by power ofthe internal combustion engine, and a second pump [electric oil pump 35]to be driven by a power source [motor] independent of the power transferpath. The oil supply device further includes a first supply oil passage[lubrication oil passage 33L of the transmission 33 and oil passage onits upstream side] through which oil discharged from the first pump issupplied to the transmission, and a second supply oil passage[lubrication oil passage K0L of the clutch K0 and oil passage on itsupstream side] through which oil discharged from the second pump issupplied to the friction engagement device.

In the oil supply device of JP 2015-197146 A, both the oil dischargedfrom the first pump and the oil discharged from the second pump aresupplied to a hydraulic pressure regulating valve [regulator valve 43].A cooler configured to cool oil is provided on a downstream side of thehydraulic pressure regulating valve in the first supply oil passage.Therefore, the cooler cools only a part of the oil supplied to thehydraulic pressure regulating valve and discharged to the downstreamside when a set hydraulic pressure [line pressure PL] is generated.

In this structure, the amount of oil to be actually supplied to thecooler depends on the magnitude of the set hydraulic pressure. Forexample, when the set hydraulic pressure is high and the amount of oildischarged to the downstream side is small, the oil cannot be cooledsufficiently. Particularly in a state in which the internal combustionengine is stopped and the first pump is not driven, the oil dischargedfrom the second pump and supplied to the friction engagement devicecannot be cooled sufficiently. Thus, there is a possibility that thefriction engagement device cannot be cooled sufficiently.

SUMMARY

An exemplary aspect of the disclosure attains an oil supply device inwhich oil can be cooled sufficiently irrespective of a travelingcondition of a vehicle.

An oil supply device disclosed herein is an oil supply device to beprovided in a vehicular drive transmission device including a frictionengagement device and a transmission in order from an internalcombustion engine side in a power transfer path connecting an internalcombustion engine to a wheel. The oil supply device includes: a firstpump configured to discharge oil by being driven by power transferredalong the power transfer path; a second pump configured to discharge theoil by being driven by a power source independent of the power transferpath; a first supply oil passage through which the oil discharged fromthe first pump is supplied to the transmission; and a second supply oilpassage through which the oil discharged from the second pump issupplied to the friction engagement device.

The first supply oil passage and the second supply oil passage have acommon portion partially common to the first supply oil passage and thesecond supply oil passage. A cooler configured to cool the oil isprovided in the common portion. The oil supply device includes a firstselector valve configured to choose whether the oil discharged from thefirst pump flows into the common portion, and a second selector valveconfigured to choose whether the oil passing through the common portionflows into the transmission.

According to this structure, the cooler is provided in the commonportion of the first supply oil passage and the second supply oilpassage. Therefore, both the oil to be discharged from the first pumpand supplied to the transmission and the oil to be discharged from thesecond pump and supplied to the friction engagement device can be cooledappropriately. At this time, a state in which the oil discharged fromthe first pump is cooled by the cooler and a state in which the oildischarged from the second pump is cooled by the cooler without causingthe oil discharged from the first pump to flow into the common portioncan be switched by appropriately switching a state of the first selectorvalve. Further, a state in which the oil cooled by the cooler flows intothe transmission and a state in which the oil cooled by the cooler flowsinto the friction engagement device without the oil flowing into thetransmission can be switched by appropriately switching a state of thesecond selector valve. Thus, the oil can appropriately be supplied toeach portion of the vehicular drive transmission device whilesufficiently cooling the oil irrespective of the traveling condition ofthe vehicle.

Further features and advantages of the technology disclosed herein willbecome more apparent from the following description of illustrative andnon-limiting embodiments with reference to the drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic diagram illustrating the overall structure of avehicular drive transmission device of a first embodiment.

FIG, 2 is a schematic diagram of an oil supply device.

FIG. 3 is a schematic diagram illustrating an example of how oil issupplied when a starting clutch is mildly cooled. FIG. 4 is a schematicdiagram illustrating an example of how the oil is supplied when thestarting clutch is intensively cooled.

FIG. 5 is a schematic diagram of an oil supply device of a secondembodiment.

FIG. 6 is a schematic diagram illustrating an example of how oilsupplied in a first state of a common spool valve.

FIG. 7 is a schematic diagram illustrating an example of how the oil issupplied in a second state of the common spool valve.

DETAILED DESCRIPTION OF EMBODIMENTS First Embodiment

A first embodiment of an oil supply device is described with referenceto the drawings. An oil supply device 1 of this embodiment is providedin a vehicular drive transmission device 9 and used in the vehiculardrive transmission device 9.

As illustrated in FIG. 1, the vehicular drive transmission device 9 isprovided between an internal combustion engine EG and wheels W invarious vehicles such as a hybrid vehicle. The vehicular drivetransmission device 9 of this embodiment includes an input shaft 91, astarting clutch 92, an intermediate shaft 93, a rotating electricalmachine 94, a transmission 95, an output shaft 96, and a differentialgear device 97. The starting clutch 92, the rotating electrical machine94, the transmission 95, and the differential gear device 97 areprovided in the stated order from the internal combustion engine EG sidein a power transfer path connecting the internal combustion engine EG tothe wheels W. These components are housed in an unillustrated case(drive apparatus case).

The input shaft 91 is coupled to the internal combustion engine EG so asto rotate together with the internal combustion engine EG. For example,the starting clutch 92 is structured by a hydraulic-drive frictionclutch. The starting clutch 92 is interposed between the input shaft 91and the intermediate shaft 93. In an engagement state (direct engagementstate in this case), the starting clutch 92 causes the input shaft 91and the intermediate shaft 93 to rotate together. In a disengagementstate, the starting clutch 92 interrupts power transfer between theinput shaft 91 and the intermediate shaft 93. The starting clutch 92 maybe brought into a slip engagement state in which friction plates 92Pengage while slipping. In the slip engagement state, power istransferred from a higher rotation speed side to a lower rotation speedside while the input shaft 91 and the intermediate shaft 93 are rotatingrelative to each other. In this embodiment, the starting clutch 92corresponds to a “friction engagement device”.

The intermediate shaft 93 is connected to the rotating electricalmachine 94. The rotating electrical machine 94 functions as a drivesource for the wheels W in cooperation with the internal combustionengine EG. The rotating electrical machine 94 includes a stator fixed tothe case, and a rotor rotatably supported on a radially inner side ofthe stator. The rotor of the rotating electrical machine 94 is coupledto the intermediate shaft 93 so as to rotate together with theintermediate shaft 93.

The intermediate shaft 93 is coupled to an input side of thetransmission 95 as an input member (shifting input member) of thetransmission 95. For example, the transmission 95 may be a steppedautomatic transmission configured to switch a plurality of shift speeds,or a stepless automatic transmission configured to change speed ratiossteplessly. In the case of the stepped automatic transmission, it isappropriate that the transmission 95 be provided with, for example, aplanetary gear mechanism and shifting engagement devices (clutches andbrakes). The transmission 95 may have a single-axis structure or amulti-axis structure. In the case of the multi-axis structure, it isappropriate that the transmission 95 be provided with, for example, acounter gear mechanism. The transmission 95 shifts rotation of theintermediate shaft 93 serving as the shifting input member based on aspeed ratio in response to the condition of the transmission 95, andoutputs the rotation from the output shaft 96 serving also as an outputmember (shifting output member) of the transmission 95.

The output shaft 96 is coupled to the differential gear device 97, andalso to the pair of right and left wheels W via the differential geardevice 97 and a pair of right and left axles.

The vehicular drive transmission device 9 of this embodiment includesthe oil supply device 1 including a first pump 11 and a second pump 12in order to supply oil to each portion of the vehicular drivetransmission device 9. For example, an internal or external gear pump ora vane pump may be used as the first pump 11 without particularlimitation. For example, an internal or external gear pump or a vanepump may similarly be used as the second pump 12 without particularlimitation.

The first pump 11 is a mechanical oil pump to be driven by powertransferred along the power transfer path connecting the internalcombustion engine EG to the wheels W. As illustrated in FIG. 1, thefirst pump 11 is coupled to the input shaft 91 and the intermediateshaft 93 via a power source switching mechanism 98. The power sourceswitching mechanism 98 is structured by a pair of one-way clutches. Inthis example, one of the one-way clutches is interposed between thefirst pump 11 and the input shaft 91, and the other one-way clutch isinterposed between the first pump 11 and the intermediate shaft 93. Thefirst pump 11 discharges oil by being driven by a power source that isthe input shaft 91 or the intermediate shaft 93 having a higher rotationspeed.

The second pump 12 is an electric oil pump to be driven by power of anelectric motor 99 independent of the power transfer path connecting theinternal combustion engine EG to the wheels W. In this embodiment, theelectric motor 99 corresponds to a “power source independent of thepower transfer path”.

As illustrated in FIG. 2, the oil supply device 1 of this embodimentsupplies oil discharged from at least one of the first pump 11 and thesecond pump 12 to the starting clutch 92, the transmission 95, therotating electrical machine 94, and the like. The oil supply device 1includes the first pump 11, the second pump 12, a first pressureregulating valve 21, a second pressure regulating valve 22, a firstsupply oil passage S1, and a second supply oil passage S2 as mainconstituent elements. The first supply oil passage S1 is an oil passagethrough which the oil discharged from the first pump 11 is supplied tothe transmission 95 (specifically, gears included in the planetary gearmechanism and the counter gear mechanism). The first supply oil passageS1 includes a first reference pressure oil passage 41, a secondreference pressure oil passage 42, and a lubrication oil passage 43. Thesecond supply oil passage S2 is an oil passage through which the oildischarged from the second pump 12 is supplied to the starting clutch 92(specifically, the friction plates 92P). The second supply oil passageS2 includes a subsidiary reference pressure oil passage 51 and acooling/lubrication oil passage 52.

The first pump 11 sucks the oil (ATF; Automatic transmission fluid) froman oil pan provided at the bottom of the case, and discharges the oilwhile increasing the pressure to a predetermined pressure. One end ofthe first reference pressure oil passage 41 is connected to a dischargeport of the first pump 11. The other end of the first reference pressureoil passage 41 is connected to an input port of the first pressureregulating valve 21.

The first pressure regulating valve 21 (primary regulator valve) isstructured by a relief pressure reducing valve. The first pressureregulating valve 21 regulates a hydraulic pressure in the firstreference pressure oil passage 41 located on an upstream side of thefirst pressure regulating valve 21 to be a line pressure PL bydischarging, to a downstream side, a part of the oil discharged from thefirst pump 11 (or the second pump 12). In this embodiment, the firstpressure regulating valve 21 corresponds to a “hydraulic pressureregulating valve”, and the line pressure PL corresponds to a “sethydraulic pressure”. The first pressure regulating valve 21 discharges(drains) surplus oil generated through pressure regulation from a firstdrain port and a second drain port. The oil from the first drain port issupplied to the second. pressure regulating valve 22 through the secondreference pressure oil passage 42. The oil from the second drain port isreturned to the first pump 11 (and the second pump 12) through a returnoil passage (represented by “SUC” in FIG. 2).

The second pressure regulating valve 22 (secondary regulator valve) isstructured by a relief pressure reducing valve. The second pressureregulating valve 22 discharges, to a downstream side, a part of the oildischarged from the first pump 11 (or the second pump 12) and then fromthe first drain port of the first pressure regulating valve 21. Thesecond pressure regulating valve 22 regulates a hydraulic pressure inthe second reference pressure oil passage 42 located on an upstream sideof the second pressure regulating valve 22 to be a secondary pressurePsec lower than the line pressure PL. The second pressure regulatingvalve 22 discharges (drains) surplus oil generated through pressureregulation from a first drain port and a second drain port. The oil fromthe first drain port is supplied to the gears and the like in thetransmission 95 through the lubrication oil passage 43. The oil from thesecond drain port is returned to the first pump 11 (and the second pump12) through a return oil passage (represented by “SUC” in FIG. 2).

A cooler 25 and a first selector valve 31 are provided in the secondreference pressure oil passage 42. The first selector valve 31 isprovided on an upstream side (first pump 11 side) of the cooler 25. Thefirst selector valve 31 is structured by an on-off valve. The firstselector valve 31 switches an open state for permitting a flow of theoil in the second reference pressure oil passage 42 and a closed statefor interrupting the flow of the oil. The cooler 25 reduces an oiltemperature by cooling the oil flowing through the cooler 25 by heatexchange. A second selector valve 32 is provided in the lubrication oilpassage 43. The second selector valve 32 is structured by a relay valveconfigured to switch source flow passages of the oil that flows towardthe transmission 95. A “throttle” is provided in the lubrication oilpassage 43 by an orifice 71.

One end of a first bypass oil passage 46 and one end of a second bypassoil passage 47 are connected to the second reference pressure oilpassage 42. The one end of the first bypass oil passage 46 is connectedto a third connection point c located on a downstream side of the firstpressure regulating valve 21 and on an upstream side of the firstselector valve 31. The other end of the first bypass oil passage 46 isconnected to the lubrication oil passage 43 via the second selectorvalve 32. Thus, the first bypass oil passage 46 is connected in parallelto the first supply oil passage S1 while bypassing the first selectorvalve 31, the cooler 25, and the second pressure regulating valve 22. A“throttle” is provided in the first bypass oil passage 46 by an orifice72.

The one end of the second bypass oil passage 47 is connected to a secondconnection point b located on the downstream side of the first pressureregulating valve 21 and on an upstream side of the first selector valve31 and the third connection point c. The other end of the second bypassoil passage 47 is connected to a seventh connection point g located on adownstream side of the second selector valve 32. Thus, the second bypassoil passage 47 is connected in parallel to the first supply oil passageS1 while bypassing the first selector valve 31, the cooler 25, thesecond pressure regulating valve 22, and the second selector valve 32. A“throttle” is provided in the second bypass oil passage 47 by orifices73. In this embodiment, the first bypass oil passage 46 and the secondbypass oil passage 47 correspond to a “bypass oil passage”.

Similarly to the first pump 11, the second pump 12 sucks the oil fromthe oil pan at the bottom of the case, and discharges the oil whileincreasing the pressure to a predetermined pressure. One end of thesubsidiary reference pressure oil passage 51 is connected to a dischargeport of the second pump 12. The other end of the subsidiary referencepressure oil passage 51 is connected to the second reference pressureoil passage 42. In this embodiment, the subsidiary reference pressureoil passage 51 is connected to a fourth connection point d located on adownstream side of the first selector valve 31 and on an upstream sideof the cooler 25 in the second reference pressure oil passage 42.

A third selector valve 33 is provided in the subsidiary referencepressure oil passage 51. The third selector valve 33 is structured by arelay valve configured to switch destination flow passages to which theoil discharged from the second pump 12 flows. The oil from a firstoutput port of the third selector valve 33 is supplied to the secondreference pressure oil passage 42 and the second pressure regulatingvalve 22 through the subsidiary reference pressure oil passage 51. Oneend of a connection oil passage 66 is connected to a second output portof the third selector valve 33. The other end of the connection oilpassage 66 is connected to the first reference pressure oil passage 41.The connection oil passage 66 is connected to a first connection point alocated on the upstream side of the first pressure regulating valve 21in the first reference pressure oil passage 41. The oil from the secondoutput port of the third selector valve 33 is supplied to the firstreference pressure oil passage 41 and the first pressure regulatingvalve 21 through the connection oil passage 66.

The cooling/lubrication oil passage 52 that structures the second supplyoil passage S2 in cooperation with the subsidiary reference pressure oilpassage 51 is an oil passage through which the oil is supplied to thefriction plates 92P of the starting clutch 92 in order to cool andlubricate the friction plates 92P. The cooling/lubrication oil passage52 branches from the second reference pressure oil passage 42 at a sixthconnection point f located on a downstream side of the cooler 25 and onthe upstream side of the second pressure regulating valve 22 in thesecond reference pressure oil passage 42. A fourth selector valve 34 isprovided in the cooling/lubrication oil passage 52. The fourth selectorvalve 34 is structured by an on-off valve. The fourth selector valve 34switches an open state for permitting a flow of the oil in thecooling/lubrication oil passage 52 and a closed state for interruptingthe flow of the oil. A “throttle” is provided in the cooling/lubricationoil passage 52 by an orifice 74.

As described above, in this embodiment, both the subsidiary referencepressure oil passage 51 and the cooling/lubrication oil passage 52 thatstructure the second supply oil passage S2 are connected to the secondreference pressure oil passage 42 that structures the first supply oilpassage S1. Further, the subsidiary reference pressure oil passage 51 isconnected to the fourth connection point d located on the upstream sideof the cooler 25 in the second reference pressure oil passage 42, andthe cooling/lubrication oil passage 52 is connected to the sixthconnection point f located on the downstream side of the cooler 25 inthe second reference pressure oil passage 42. That is, in thisembodiment, the first supply oil passage S1 and the second supply oilpassage S2 have a common portion CP partially common to the first supplyoil passage S1 and the second supply oil passage S2. The cooler 25 isprovided in the common portion CP. In this example, the common portionCP of the first supply oil passage Si and the second supply oil passageS2 is a portion ranging from the fourth connection point d to the sixthconnection point f in the second reference pressure oil passage 42.

Description is given below of relationships between the common portionCP and the first bypass oil passage 46, the second bypass oil passage47, the connection oil passage 66, the first selector valve 31, thesecond selector valve 32, and the third selector valve 33 describedabove.

The first bypass oil passage 46 and the second bypass oil passage 47 areconnected to the first supply oil passage S1 in parallel to the commonportion CP while bypassing the common portion CR The second bypass oilpassage 47 is provided so as to further bypass the first bypass oilpassage 46. The connection oil passage 66 is connected to the firstconnection point a located on the upstream side of the first pressureregulating valve 21 in the first supply oil passage S1 and to a portionlocated on an upstream side of the common portion CP in the secondsupply oil passage S2 (third selector valve 33 provided in thesubsidiary reference pressure oil passage 51).

The first selector valve 31 chooses whether the oil flowing from anupstream side of the common portion CP and the bypass oil passages 46and 47 flows into the common portion CP on a downstream side or not.That is, the first selector valve 31 chooses whether the oil dischargedfrom the first pump 11 flows into the common portion CR. In thisembodiment, the oil flows at least into the second bypass oil passage 47even if the oil flows into the common portion CR. Since the “throttle”is provided in the second bypass oil passage 47 by the orifices 73 asdescribed above and a pressure loss increases, the amount of oil flowingthrough the second bypass oil passage 47 is smaller than the amount ofoil toward the common portion CP in the state in which the oil flowsinto the common portion CP. Therefore, the first selector valve 31chooses whether the oil flows toward the downstream side or not, therebyswitching a main flow destination of the oil flowing from the upstreamside of the common portion CP and the bypass oil passages 46 and 47 tothe common portion CP or to the bypass oil passages 46 and 47.

That is, the first selector valve 31 switches a main flow destination ofthe oil flowing from the first drain port of the first pressureregulating valve 21 located on the upstream side of the bypass oilpassages 46 and 47 to the common portion CP or to the bypass oilpassages 46 and 47. In the open state, the first selector valve 31guides the oil flowing after being discharged from the first pressureregulating valve 21 to the common portion CP (majority) and to thebypass oil passages 46 and 47 (minority). In the closed state, the firstselector valve 31 guides the oil only to the bypass oil passages 46 and47. This mode is herein included in the concept that “the flowdestination of the oil flowing from the upstream side of the commonportion and the bypass oil passage is switched to the common portion orto the bypass oil passage”. The first selector valve 31 may bestructured such that the flow destination of the oil flowing from theupstream side of the common portion CP and the bypass oil passages 46and 47 is switched exclusively to the common portion CP or to the bypassoil passages 46 and 47.

The second selector valve 32 chooses whether the oil passing through thecommon portion flows into the transmission. More specifically, thesecond selector valve 32 chooses whether the oil passing through thecommon portion CP is supplied to the transmission 95 on the downstreamside or is drained. In this embodiment, the oil is supplied at least tothe starting clutch 92 through a cooling oil passage 56 and acommunication oil passage 58 described later even if the oil flows intothe transmission 95. A “throttle” is provided in the communication oilpassage 58 by orifices 76, and a pressure loss increases. Thus, theamount of oil supplied to the starting clutch 92 through the cooling oilpassage 56 and the communication oil passage 58 is smaller than theamount of oil supplied to the transmission 95 in the state in which theoil is supplied to the transmission 95. Therefore, the second selectorvalve 32 chooses whether the oil flows toward the downstream side or isdrained, thereby switching a main flow destination of the oil passingthrough the common portion CP to the transmission 95 or to the startingclutch 92.

That is, the second selector valve 32 switches a main flow destinationof the oil cooled by the cooler 25 provided in the common portion CP tothe gears and the like in the transmission 95 or to the friction plates92P of the starting clutch 92. In a first state, the second selectorvalve 32 guides both the oil flowing from the cooler 25 and the oilflowing from the first bypass oil passage 46 to the transmission 95. Ina second state, the second selector valve 32 discharges the oil flowingfrom the cooler 25, and interrupts the flow of the oil in the firstbypass oil passage 46. Thus, in the first state, the second selectorvalve 32 guides the oil flowing from the cooler 25 to the transmission95 (majority) together with the oil flowing from the first bypass oilpassage 46 and to the starting clutch 92 (friction plates 92P)(minority). In the second state, the second selector valve 32 guides theoil to the starting clutch 92 (friction plates 92P) without guiding theoil to the transmission 95. This mode is herein included in the conceptthat “the flow destination of the oil passing through the common portionis switched to the transmission or to the friction engagement device”.The second selector valve 32 may be structured such that the flowdestination of the oil passing through the common portion CP is switchedexclusively to the transmission 95 or to the starting clutch 92.

The third selector valve 33 switches a flow destination of the oildischarged from the second pump 12 to the common portion CP or to theconnection oil passage 66. The third selector valve 33 switches the flowdestination of the oil discharged from the second pump 12 to the cooler25 or to the input port of the first pressure regulating valve 21. In afirst state, the third selector valve 33 guides the oil discharged fromthe second pump 12 to the cooler 25. In a second state, the thirdselector valve 33 guides the oil to the first pressure regulating valve21. The oil supplied to the input port of the first pressure regulatingvalve 21 may be supplied to the cooler 25 from the first drain port ofthe first pressure regulating valve 21.

The oil supply device 1 of this embodiment further includes a thirdsupply oil passage S3 and a fourth supply oil passage S4. The thirdsupply oil passage S3 is an oil passage branching from a fifthconnection point e located on the downstream side of the cooler 25 inthe second supply oil passage S2 and structured such that the oilpassing through the cooler 25 is supplied to the rotating electricalmachine 94. The third supply oil passage S3 includes the cooling oilpassage 56. In the cooling oil passage 56, the oil is supplied to statorcoils, permanent magnets, and the like of the rotating electricalmachine 94 in order to cool the stator coils, the permanent magnets, andthe like. As a method for supplying the oil to the rotating electricalmachine 94, various methods may be employed, such as a method in whichthe oil is supplied by dripping down from above the stator (suppliedfrom the top), or a method in which the oil is caused to flow radiallyoutward from an oil passage formed in a rotor shaft (supplied from thecenter of the shaft). A “throttle” is provided in the cooling oilpassage 56 by an orifice 75.

In this embodiment, the communication oil passage 58 connecting thecooling oil passage 56 to the cooling/lubrication oil passage 52 throughwhich the oil is supplied to the friction plates 92P of the startingclutch 92 is further provided over the cooling oil passage 56 and thecooling/lubrication oil passage 52. The “throttle” is also provided inthe communication oil passage 58 by the orifices 76.

The fourth supply oil passage S4 is an oil passage through which the oilwhose pressure is regulated to be the line pressure PL by the firstpressure regulating valve 21 is supplied to the starting clutch 92. Thefourth supply oil passage S4 includes an engagement control oil passage61. In the engagement control oil passage 61, the oil having the linepressure PL is supplied to a hydraulic servo mechanism 92S of thestarting clutch 92 in order to control the engagement state (directengagement state/slip engagement state/disengagement state) of thestarting clutch 92. The hydraulic servo mechanism 92S may include, forexample, a linear solenoid valve configured to further regulate ahydraulic pressure by using the line pressure PL as an originalpressure. The engagement control oil passage 61 is connected to thefirst connection point a that is a portion connecting the firstreference pressure oil passage 41 to the connection oil passage 66.

For example, when the vehicle steadily travels at least by a torque ofthe internal combustion engine EU the friction plates 92P of thestarting clutch 92 are brought into press contact with each other so asto rotate together without a slip. Therefore, the heat generation amountis small, and the need for cooling is not very strong. In this case, asillustrated in FIG. 3, the first selector valve 31 is set in the openstate, the second selector valve 32 is set in the first state, the thirdselector valve 33 is set in the second state, and the fourth selectorvalve 34 is set in the closed state. Then, the oil discharged from thefirst pump 11 and the oil discharged from the second pump 12 aresupplied to the first pressure regulating valve 21 while merging witheach other, thereby generating the line pressure PL. The oil having theline pressure PL is supplied to the hydraulic servo mechanism 92S of thestarting clutch 92, and the starting clutch 92 is kept in the directengagement state.

A part of the oil discharged from the first pressure regulating valve 21for pressure regulation is cooled by the cooler 25, and the other partflows through the bypass oil passages 46 and 47. Those parts of the oilare supplied to the transmission 95 after merging with each other,thereby lubricating the gears and the like. A part of the oil cooled bythe cooler 25 is supplied to the rotating electrical machine 94 tomainly cool the stator coils, the permanent magnets, and the like, and apart of the supplied oil is also supplied to the starting clutch 92 tocool the friction plates 92P. While the vehicle is steadily traveling,the line pressure PL is relatively high, and the amount of oildischarged from the first pressure regulating valve 21 is not verylarge, but the oil suffices if the lubrication of the gears in thetransmission 95 and the cooling of the stator coils and the like of therotating electrical machine 94 can be performed appropriately. If theamount of oil discharged from the first pump 11 is sufficiently large inthe case illustrated in FIG. 3, the second pump 12 may be stopped andthe oil may be supplied to each portion from the first pump 11 alone.

For example, when the vehicle is started at least by the torque of theinternal combustion engine EG, the starting clutch 92 may be broughtinto the slip engagement state in order to smooth out differentialrotation between a synchronization rotation speed depending on a vehiclespeed and a minimum rotation speed for preventing a stall of theinternal combustion engine EG. In this case, the starting clutch 92transfers the torque of the internal combustion engine EG while thefriction plates 92P are slipping. Therefore, the heat generation amountincreases, and the need for cooling is strong. In this case, asillustrated in FIG. 4, the first selector valve 31 is set in the closedstate, the second selector valve 32 is set in the second state, thethird selector valve 33 is set in the first state, and the fourthselector valve 34 is set in the open state. Then, only the oildischarged from the first pump 11 is supplied to the first pressureregulating valve 21, and the oil discharged from the first pressureregulating valve 21 is supplied to the transmission 95 through thesecond bypass oil passage 47, thereby lubricating the gears and thelike.

The oil discharged from the second pump 12 is supplied to the cooler 25.In this case, all the oil discharged from the second pump 12 is suppliedto the cooler 25. Then, a large amount of oil cooled by the cooler 25 issupplied to the starting clutch 92 and the rotating electrical machine94 to cool the. friction plates 92P, the stator coils, and the like.When the vehicle is started, the heat generation amount may increasebecause the starting clutch 92 is brought into the slip engagementstate, but all the oil discharged from the second pump 12 is directlycooled by the cooler 25 and is supplied to the friction plates 92P,whereby the friction plates 92P that generate heat can be cooledsufficiently. Thus, overheating of the starting clutch 92 can besuppressed. When the vehicle is started., a certain magnitude of theline pressure PL is necessary, and the vehicle speed and the rotationspeed of the internal combustion engine EG are relatively low.Therefore, the amount of oil discharged from the first pressureregulating valve 21 is not very large. However, the oil suffices if thegears in the transmission 95 can be lubricated appropriately.

Second Embodiment

A second embodiment of the oil supply device is described with referenceto the drawings. In this embodiment, the specific structures of theselector valve and the bypass oil passage differ from those in the firstembodiment. The oil supply device of this embodiment is described belowfocusing on the differences from the first embodiment. The matters thatare not particularly described are similar to those in the firstembodiment, and the same reference symbols are assigned to omitdetailed. description.

As illustrated in FIG. 5, the oil supply device 1 of this embodimentsupplies the oil discharged from at least one of the first pump 11 andthe second pump 12 to the starting clutch 92, the transmission 95, therotating electrical machine 94, and the like. The oil supply device 1includes the first pump 11, the second pump 12, the first pressureregulating valve 21, a common spool valve 36, the first supply oilpassage S1, and the second supply oil passage 52 as main constituentelements. The first supply oil passage S1 includes the first referencepressure oil passage 41, a heat exchange oil passage 44, and thelubrication oil passage 43. The second supply oil passage 52 includesthe subsidiary reference pressure oil passage 51 and thecooling/lubrication oil passage 52.

The one end of the first reference pressure oil passage 41 is connectedto the discharge port of the first pump 11. The other end of the firstreference pressure oil passage 41 is connected to the input port of thefirst pressure regulating valve 21. The first pressure regulating valve21 regulates the hydraulic pressure in the first reference pressure oilpassage 41 located on the upstream side of the first pressure regulatingvalve 21 to be the line pressure PL by discharging, to the downstreamside, a part of the oil discharged from the first pump 11 (or the secondpump 12).

In this embodiment, the second pressure regulating valve 22 configuredto generate the secondary pressure Psec from the line pressure PL is notprovided. One end of the heat exchange oil passage 44 is connected tothe first drain port of the first pressure regulating valve 21. The oilfrom the first drain port of the first pressure regulating valve 21 issupplied to the gears and the like in the transmission 95 through theheat exchange oil passage 44 and the lubrication oil passage 43.

The cooler 25 and the common spool valve 36 are provided in the heatexchange oil passage 44. The common spool valve 36 is provided on theupstream side (first pump 11 side) of the cooler 25. The common spoolvalve 36 is structured by a spool valve having a spool. An upstreamportion of the heat exchange oil passage 44 is connected to a thirdinput port 36 c of the common spool valve 36, and a downstream portionof the heat exchange oil passage 44 is connected to a third output port36 g and a first input port 36 a of the common spool valve 36. Thecommon spool valve 36 is configured to switch a first state and a secondstate depending on the position of the spool. The switching of the twostates (first state/second state) is described later. The cooler 25reduces the oil temperature by cooling the oil flowing through thecooler 25 by heat exchange.

A single bypass oil passage 48 is connected to the heat exchange oilpassage 44. One end of the bypass oil passage 48 is connected to thedownstream side of the first pressure regulating valve 21 and to anupstream side of the common spool valve 36. The other end of the bypassoil passage 48 is connected to a second input port 36 b of the commonspool valve 36. The bypass oil passage 48 is connected to thelubrication oil passage 43 via the common spool valve 36. Thus, thebypass oil passage 48 is connected to the lubrication oil passage 43while bypassing the cooler 25. A “throttle” is provided in the bypassoil passage 48 by an orifice 77.

One end of the lubrication oil passage 43 is connected to a secondoutput port 36 f of the common spool valve 36. The other end of thelubrication oil passage 43 extends to the gears and the like in thetransmission 95. The “throttle” is provided in the lubrication oilpassage 43 by the orifice 71.

The one end of the subsidiary reference pressure oil passage 51 isconnected to the discharge port of the second pump 12. The other end ofthe subsidiary reference pressure oil passage 51 is connected to afourth input port 36 d of the common spool valve 36. The subsidiaryreference pressure oil passage 51 is connected alternatively to the heatexchange oil passage 44 or to the connection oil passage 66 via thecommon spool valve 36. The one end of the connection oil passage 66 isconnected to a fourth output port 36 h of the common spool valve 36. Theother end of the connection oil passage 66 is connected to the upstreamside of the first pressure regulating valve 21 in the first referencepressure oil passage 41.

One end of the cooling/lubrication oil passage 52 is connected to afirst output port 36 e of the common spool valve 36. The other end ofthe cooling/lubrication oil passage 52 extends to the friction plates92P of the starting clutch 92. The “throttle” is provided in thecooling/lubrication oil passage 52 by the orifice 74.

As described above, the common spool valve 36 is configured to switchthe first state and the second state depending on the position of thespool. In the first state, the first input port 36 a communicates withthe second output port 36 f, the third input port 36 c communicates withthe third output port 36 g, and the fourth input port 36 d communicateswith the fourth output port 36 h (see FIG. 6 as well). In the secondstate, the first input port 36 a communicates with the first output port36 e, the second input port 36 b communicates with the second outputport 36 f, and the fourth input port 36 d communicates with the thirdoutput port 36 g (see FIG. 7 as well).

Since the fourth input port 36 d communicates with the fourth outputport 36 h in the first state as illustrated in FIG. 6, the subsidiaryreference pressure oil passage 51 communicates with the connection oilpassage 66. Thus, the oil discharged from the second pump 12 is suppliedfor generation of the line pressure PL together with the oil dischargedfrom the first pump 11. Since the third input port 36 c communicateswith the third output port 36 g, the upstream portion and the downstreamportion of the heat exchange oil passage 44 communicate with each other.Thus, the oil discharged from the first pump 11 and the second pump 12and from the first drain port of the first pressure regulating valve 21when the line pressure PL is generated is supplied to the cooler 25 forcooling. Since the first input port 36 a communicates with the secondoutput port 36 f, the heat exchange oil passage 44 communicates with thelubrication oil passage 43. Thus, the oil cooled by the cooler 25 asdescribed above is supplied to the gears and the like in thetransmission 95. At this time, the oil cooled by the cooler 25 is alsosupplied to the friction plates 92P of the starting clutch 92 and to thestator coils and the like of the rotating electrical machine 94.

Since the fourth input port 36 d does not communicate with the fourthoutput port 36 h in the second state as illustrated in FIG. 7, the firstpump 11 and the second pump 12 supply the oil independently of eachother. Since the second input port 36 b communicates with the secondoutput port 36 f, the bypass oil passage 48 communicates with thelubrication oil passage 43. Thus, the oil discharged from the first pump11 and from the first drain port of the first pressure regulating valve21 when the line pressure PL is generated is supplied to the gears andthe like in the transmission 95 without passing through the cooler 25.Since the fourth input port 36 d communicates with the third output port36 g, the subsidiary reference pressure oil passage 51 communicates withthe heat exchange oil passage 44. Since the first input port 36 acommunicates with the first output port 36 e, the heat exchange oilpassage 44 communicates with the cooling/lubrication oil passage 52.Thus, the oil discharged from the second pump 12 is cooled by the cooler25 and then supplied to the friction plates 92P of the starting clutch92. At this time, the oil cooled by the cooler 25 is also supplied tothe stator coils and the like of the rotating electrical machine 94.

As described above, in this embodiment, the common spool valve 36switches the first state and the second state to choose whether the oildischarged from the first pump 11 flows into the common portion CP(cooler 25) (function of the first selector valve 31 in the firstembodiment). At this time, the common spool valve 36 chooses whether theoil passing through the common portion CP (cooler 25) flows into thegears and the like in the transmission 95 (function of the secondselector valve 32 in the first embodiment). In addition, the commonspool valve 36 chooses whether the oil passing through the commonportion CP (cooler 25) flows into the friction plates 92P of thestarting clutch 92 without passing through the communication oil passage58 (function of the fourth selector valve 34 in the first embodiment).At this time, the common spool valve 36 switches the flow destination ofthe oil discharged from the second pump 12 to the common portion CP(cooler 25) or to the connection oil passage 66 (function of the thirdselector valve 33 in the first embodiment). That is, the common spoolvalve 36 of this embodiment is an integrated valve having all thefunctions of the first selector valve 31, the second selector valve 32,the third selector valve 33, and the fourth selector valve 34 describedin the first embodiment. Therefore, in this embodiment, the common spoolvalve 36 corresponds to the “first selector valve”, the “second selectorvalve”, and the “third selector valve”.

Other Embodiments

(1) In the first embodiment described above, description is given of theexemplary structure in which the second selector valve 32 is configuredto change stepwise the amount of oil that flows toward the transmission95. However, the present disclosure is not limited to this structure.The second selector valve 32 may be structured such that the amount ofoil to be caused to flow toward the transmission 95 can be changedcontinuously; including “zero”.

(2) In the first embodiment described above, description is given of theexample in which the third selector valve 33 is structured by the relayvalve provided in the subsidiary reference pressure oil passage 51.However, the present disclosure is not limited to this structure. Forexample, the third selector valve 33 may be structured by an on-offvalve provided in the connection oil passage 66.

(3) In the first embodiment described above, description is given of theexample in which the first selector valve 31, the second selector valve32, the third selector valve 33, and the fourth selector valve 34 arestructured as independent selector valves. In the second embodiment,description is given of the example in which all the selector valves arestructured by the integrated valve (common spool valve 36). However, thepresent disclosure is not limited to this structure. For example, onlythe first selector valve 31 and the second selector valve 32 may bestructured by the integrated valve (for example, the common spoolvalve). Alternatively, only the first selector valve 31, the secondselector valve 32, and the third selector valve 33 may be structured bythe integrated valve. In addition, any combination of two or threeselector valves out of the first selector valve 31, the second selectorvalve 32, the third selector valve 33, and the fourth selector valve 34may be structured by the integrated valve.

(4) In the first embodiment described above, description is given of theexemplary structure in which the oil supply device 1 is provided withthe second pressure regulating valve 22 configured to generate thesecondary pressure Psec. However, the present disclosure is not limitedto this structure. As in the second embodiment, the second pressureregulating valve 22 need not essentially be provided.

(5) In the embodiments described above, description is given of theexemplary structure in which the first pump 11 is driven by the inputshaft 91 or the intermediate shaft 93 having a higher rotation speed.However, the present disclosure is not limited to this structure. Forexample, the first pump 11 may be driven solely by the input shaft 91 orsolely by the intermediate shaft 93. Alternatively, the first pump 11may be driven solely by, for example, the output shaft 96.

(6) In the embodiments described above, description is given of theexemplary oil supply device 1 for use in the vehicular drivetransmission device 9 in which the dedicated starting clutch 92 isprovided between the input shaft 91 and the intermediate shaft 93.However, the present disclosure is not limited to this structure. Forexample, the oil supply device 1 may be used in a vehicular drivetransmission device 9 in which a hydraulic coupling (such as a torqueconverter or a fluid coupling) having a lock-up clutch is providedbetween the input shaft 91 and the intermediate shaft 93. In thisstructure, the lock-up clutch corresponds to the “friction engagementdevice”.

(7) In the embodiments described above, description is given of theexemplary structure in which the vehicular drive transmission device 9provided with the oil supply device 1 is a drive transfer apparatus fora hybrid vehicle. However, the present disclosure is not limited to thisstructure. The oil supply device 1 may be used in a drive transferapparatus for a so-called engine vehicle in which the rotatingelectrical machine 94 is not provided.

(8) The structures disclosed in the embodiments described above(including the embodiments described above and the other embodiments;the same applies hereinafter) are also applicable in combination withthe structures disclosed in the other embodiments without causing anycontradiction. Regarding other structures as well, the embodimentsdisclosed herein are illustrative in all respects. Thus, modificationsmay be made as appropriate without departing from the spirit of thedisclosure.

SUMMARY OF EMBODIMENTS

To summarize the above, the oil supply device disclosed hereinpreferably has the following structures.

The oil supply device (1) is provided in the vehicular drivetransmission device (9) including the friction engagement device (92)and the transmission (95) in order from the internal combustion engine(EG) side in the power transfer path connecting the internal combustionengine (EG) to the wheels (W). The oil supply device (1) includes:

-   -   the first pump (11) configured to discharge the oil by being        driven by the power transferred along the power transfer path;    -   the second pump (12) configured to discharge the oil by being        driven by the power source (99) independent of the power        transfer path;    -   the first supply oil passage (S1) through which the oil        discharged from the first pump (11) is supplied to the        transmission (95); and    -   the second supply oil passage (S2) through which the oil        discharged from the second pump (12) is supplied to the friction        engagement device (92).

The first supply oil passage (S1) and the second supply oil passage (S2)have the common portion (CP) partially common to the first supply oilpassage (S1) and the second supply oil passage (S2).

The cooler (25) configured to cool the oil is provided in the common.portion (CP).

The oil supply device (1) includes the first selector valve (31)configured to choose whether the oil discharged from the first pump (11)flows into the common portion (CP), and the second selector valve (32)configured to choose whether the oil passing through the common portionflows into the transmission (95).

According to this structure, the cooler (25) is provided in the commonportion (CP) of the first supply oil passage (S1) and the second supplyoil passage (S2). Therefore, both the oil to be discharged from thefirst pump (11) and supplied to the transmission (95) and the oil to bedischarged from the second pump (12) and supplied to the frictionengagement device (92) can be cooled appropriately. At this time, thestate in which the oil discharged from the first pump (11) is cooled bythe cooler (25) and the state in which the oil discharged from thesecond pump (12) is cooled by the cooler (25) without causing the oildischarged from the first pump (11) to flow into the common portion (CP)can be switched by appropriately switching the state of the firstselector valve (31). Further, the state in which the oil cooled by thecooler (25) flows into the transmission (95) and the state in which theoil cooled by the cooler (25) flows into the friction engagement device(92) without the oil flowing into the transmission (95) can be switchedby appropriately switching the state of the second selector valve (32).Thus, the oil can appropriately be supplied to each portion of thevehicular drive transmission device (9) while sufficiently cooling theoil irrespective of the traveling condition of the vehicle.

As one aspect, the following structure is preferable.

The bypass oil passage (46, 47, 48) that bypasses the common portion(CP) is connected to the first supply oil passage (S1).

The first selector valve (31) is configured to choose whether the oildischarged from the first pump (11) flows into the common portion (CP)to switch the flow destination of the oil flowing from the upstream sideof the common portion (CP) and the bypass passage (46, 47, 48) to thecommon portion (CP) or to the bypass oil passage (46, 47, 48).

According to this structure, when the oil discharged from the first pump(11) is not caused to flow into the common portion (CP), the oil can hecaused to flow into the bypass oil passage (46, 47, 48). Thus, it ispossible to switch the state in which the oil discharged from the firstpump (11) is supplied to the transmission (95) while passing through thebypass oil passage (46, 47, 48) (that is, without cooling the oil) andthe state in which the oil discharged from the first pump (11) is cooledby the cooler (25) and supplied to the transmission (95).

As one aspect, the following structure is preferable.

The hydraulic pressure regulating valve (21) configured to regulate thehydraulic pressure on the upstream side to be the set hydraulic pressure(PL) by discharging, to the downstream side, a part of the oildischarged from the first pump (11) is provided on the upstream side ofthe connection point between the first supply oil passage (S1) and thebypass oil passage (46, 47, 48),

According to this structure, the oil discharged to the downstream sidewhen the hydraulic pressure regulating valve (21) regulates thehydraulic pressure on its upstream side to be the set hydraulic pressure(PL) is supplied to the cooler (25) provided in the common portion (CP)located on the downstream side of the bypass oil passage (46, 47, 48).Therefore, the amount of oil cooled by the cooler (25) is relativelysmall, and depends on the magnitude of the set hydraulic pressure (PL).Thus, there is a relatively strong possibility that the oil cannot becooled sufficiently. In this respect, according to the technologydisclosed herein, the oil discharged from the second pump (12) candirectly be supplied to the cooler (25) without passing through thehydraulic pressure regulating valve (21). Thus, a large amount of oilcan be supplied to the cooler (25) and cooled sufficiently irrespectiveof the magnitude of the set hydraulic pressure (PL).

As one aspect, it is preferable that the oil supply device (1) furtherinclude:

-   -   the connection oil passage (66) connecting the portion located        on the upstream side of the hydraulic pressure regulating valve        (21) in the first supply oil passage (S1) to the portion located        on the upstream. side of the common portion (CP) in the second        supply oil passage (52); and    -   the third selector valve (33) configured to switch the flow        destination of the oil discharged from the second pump (12) to        the common portion (CP) or to the connection oil passage (66).

According to this structure, the state in which the oil discharged fromthe second pump (12) is directly supplied to the cooler (25) withoutpassing through the hydraulic pressure regulating valve (21) and thestate in which the oil discharged from the second pump (12) is suppliedto the hydraulic pressure regulating valve (21) can be switched byappropriately switching the state of the third selector valve (33). Inthe latter state, for example, it is possible to generate the sethydraulic pressure (PL) even in a state in which the first pump (11) isnot driven, and to avoid a decrease in fuel efficiency of the vehicledue to excessive supply of cold oil to the friction engagement device(92) in a situation in which the need for cooling of the frictionengagement device (92) is not very strong.

As one aspect, the following structure is preferable.

The second selector valve (32) is configured to choose whether the oilpassing through the common portion (CP) flows into the transmission (95)to switch the flow destination of the oil passing through the commonportion (CP) to the transmission (95) or to the friction engagementdevice (92).

According to this structure, when the oil passing through the commonportion (CP) is not caused to flow into the transmission (95), the oilcan be caused to flow into the friction engagement device (92). Thus, itis possible to switch the state in which the oil cooled by the cooler(25) is supplied to the transmission (95) and the state in which the oilis supplied to the friction engagement device (92). Accordingly, boththe transmission (95) and the friction engagement device (92) can becooled sufficiently by the oil sufficiently cooled by the cooler (25).

As one aspect, the following structure is preferable.

The vehicular drive transmission device (9) further includes therotating electrical machine (94) provided in the power transfer path andconfigured to drive the wheels (W).

The oil supply device (1) further includes the third supply oil passage(S3) branching from the portion located on the downstream side of thecooler (25) in the second supply oil passage (S2) and structured suchthat the oil passing through the cooler (25) is supplied to the rotatingelectrical machine (94).

According to this structure, the rotating electrical machine (94)together with the friction engagement device (92) can be cooledsufficiently by the oil sufficiently cooled by the cooler (25).

As one aspect, the following structure is preferable.

The first selector valve (31) and the second selector valve (32) arestructured by the common spool valve (36) having the common spool.

According to this structure, costs can be reduced by reducing the numberof components as compared to the structure in which the first selectorvalve (31) and the second selector valve (32) are provided independentlyof each other.

As one aspect, the following structure is preferable.

The first selector valve (31), the second selector valve (32), and thethird selector valve (33) are structured by the common spool valve (36)having the common spool.

According to this structure, costs can be reduced by reducing the numberof components as compared to the structure in which the first selectorvalve (31), the second selector valve (32), and the third selector valve(33) are provided independently of each other.

As one aspect, the following structure is preferable.

The common spool valve (36) is configured to switch the first state andthe second state depending on the position of the spool.

In the first state, the oil discharged from the first pump (11) iscooled by the cooler and then supplied to the transmission (95), and theoil discharged from the second pump (12) is supplied to the connectionoil passage (66).

In the second state, the oil discharged from the first pump (11) issupplied to the transmission (95) through the bypass oil passage (48),and the oil discharged from the second pump (12) is cooled by the cooler(25) and then supplied to the friction engagement device (92).

According to this structure, the state in which the oil discharged fromthe first pump (11) and the second pump (12) is cooled and then suppliedto the transmission (95) and the state in which the oil discharged fromthe first pump (11) is supplied to the transmission (95) without coolingthe oil and the oil discharged from the second pump (12) is cooled andthen supplied to the friction engagement device (92) can easily beswitched by simply switching the two positions of the spool of thecommon spool valve (36).

The oil supply device (1) is provided in the vehicular drivetransmission device (9) including the friction engagement device (92)and the transmission (95) in order from the internal combustion engine(EG) side in the power transfer path connecting the internal combustionengine (EG) to the wheels (W). The oil supply device (1) includes:

-   -   the first pump (11) configured to discharge the oil by being        driven by the power transferred along the power transfer path;    -   the second pump (12) configured to discharge the oil by being        driven by the power source (99) independent of the power        transfer path;    -   the first supply oil passage (S1) through which the oil        discharged from the first pump (11) is supplied to the        transmission (95); and    -   the second supply oil passage (S2) through which the oil        discharged from the second pump (12) is supplied to the friction        engagement device (92).

The first supply oil passage (S1) and the second supply oil passage (S2)have the common portion (CP) partially common to the first supply oilpassage (S1) and the second supply oil passage (S2).

The cooler (25) configured to cool the oil is provided in the commonportion (CP), and the bypass oil passage (46, 47) that bypasses thecommon portion (CP) is connected to the first supply oil passage (S1) inparallel to the common portion (CP).

The oil supply device (1) includes the first selector valve (31)configured to switch the flow destination of the oil flowing from theupstream side of the common portion (CP) and the bypass oil passage (46,47) to the common portion (CP) or to the bypass oil passage (46, 47),and the second selector valve (32) configured to switch the flowdestination of the oil passing through the common portion (CP) to thetransmission (95) or to the friction engagement device (92).

According to this structure, the cooler (25) is provided in the commonportion (CP) of the first supply oil passage (S1) and the second supplyoil passage (S2).

Therefore, both the oil to be discharged from the first pump (11) andsupplied to the transmission (95) and the oil to be discharged from thesecond pump (12) and supplied to the friction engagement device (92) canbe cooled appropriately. At this time, the state in which the oildischarged from the second pump (12) is cooled by the cooler (25) andsupplied to the friction engagement device (92) and the oil dischargedfrom the first pump (11) is supplied to the transmission (95) via thebypass oil passage (46, 47) and the state in which the oil dischargedfrom the first pump (11) is cooled by the cooler (25) and supplied tothe transmission (95) can be switched by appropriately switching thestates of the first selector valve (31) and the second selector valve(32). Thus, the oil can appropriately be supplied to each portion of thevehicular drive transmission device (9) while sufficiently cooling theoil irrespective of the traveling condition of the vehicle. inparticular, the friction engagement device (92) can be cooledappropriately and sufficiently.

The oil supply device disclosed herein suffices if at least one of theeffects described above can be attained.

1-9. (canceled)
 10. An oil supply device to be provided in a vehiculardrive transmission device including a friction engagement device and atransmission in order from an internal combustion engine side in a powertransfer path connecting an internal combustion engine to a wheel, theoil supply device comprising: a first pump configured to discharge oilby being driven by power transferred along the power transfer path; asecond pump configured to discharge the oil by being driven by a powersource independent of the power transfer path; a first supply oilpassage through which the oil discharged from the first pump is suppliedto the transmission; and a second supply oil passage through which theoil discharged from the second pump is supplied to the frictionengagement device, wherein: the first supply oil passage and the secondsupply oil passage have a common portion partially common to the firstsupply oil passage and the second supply oil passage, a coolerconfigured to cool the oil is provided in the common portion, and theoil supply device includes a first selector valve configured to choosewhether the oil discharged from the first pump flows into the commonportion, and a second selector valve configured to choose whether theoil passing through the common portion flows into the transmission. 11.The oil supply device according to claim 10, wherein: a bypass oilpassage that bypasses the common portion is connected to the firstsupply oil passage, and the first selector valve is configured to choosewhether the oil discharged from the first pump flows into the commonportion to switch a flow destination of the oil flowing from an upstreamside of the common portion and the bypass oil passage to the commonportion or to the bypass oil passage.
 12. The oil supply deviceaccording to claim 11, wherein a hydraulic pressure regulating valveconfigured to regulate a hydraulic pressure on an upstream side to be aset hydraulic pressure by discharging, to a downstream side, a part ofthe oil discharged from the first pump is provided on an upstream sideof a connection point between the first supply oil passage and thebypass oil passage.
 13. The oil supply device according to claim 12,further comprising: a connection oil passage connecting a portionlocated on an upstream side of the hydraulic pressure regulating valvein the first supply oil passage to a portion located on an upstream sideof the common portion in the second supply oil passage; and a thirdselector valve configured to switch a flow destination of the oildischarged from the second pump to the common portion or to theconnection oil passage.
 14. The oil supply device according to claim 13,wherein the second selector valve is configured to choose whether theoil passing through the common portion flows into the transmission toswitch a flow destination of the oil passing through the common portionto the transmission or to the friction engagement device.
 15. The oilsupply device according to claim 14, wherein: the vehicular drivetransmission device further includes a rotating electrical machineprovided in the power transfer path and configured to drive the wheel,and the oil supply device further includes a third supply oil passagebranching from a portion located on a downstream side of the cooler inthe second supply oil passage and structured such that the oil passingthrough the cooler is supplied to the rotating electrical machine. 16.The oil supply device according to claim 15, wherein the first selectorvalve and the second selector valve are structured by a common spoolvalve having a common spool.
 17. The oil supply device according toclaim 10, wherein the second selector valve is configured to choosewhether the oil passing through the common portion flows into thetransmission to switch a flow destination of the oil passing through thecommon portion to the transmission or to the friction engagement device.18. The oil supply device according to claim 10, wherein: the vehiculardrive transmission device further includes a rotating electrical machineprovided in the power transfer path and configured to drive the wheel,and the oil supply device further includes a third supply oil passagebranching from a portion located on a downstream side of the cooler inthe second supply oil passage and structured such that the oil passingthrough the cooler is supplied to the rotating electrical machine. 19.The oil supply device according to claim 10, wherein the first selectorvalve and the second selector valve are structured by a common spoolvalve having a common spool.
 20. The oil supply device according toclaim 11, wherein the second selector valve is configured to choosewhether the oil passing through the common portion flows into thetransmission to switch a flow destination of the oil passing through thecommon portion to the transmission or to the friction engagement device.21. The oil supply device according to claim 11, wherein: the vehiculardrive transmission device further includes a rotating electrical machineprovided in the power transfer path and configured to drive the wheel,and the oil supply device further includes a third supply oil passagebranching from a portion located on a downstream side of the cooler inthe second supply oil passage and structured such that the oil passingthrough the cooler is supplied to the rotating electrical machine. 22.The oil supply device according to claim 11, wherein the first selectorvalve and the second selector valve are structured by a common spoolvalve having a common spool.
 23. The oil supply device according toclaim 12, wherein the second selector valve is configured to choosewhether the oil passing through the common portion flows into thetransmission to switch a flow destination of the oil passing through thecommon portion to the transmission or to the friction engagement device.24. The oil supply device according to claim 12, wherein: the vehiculardrive transmission device further includes a rotating electrical machineprovided in the power transfer path and configured to drive the wheel,and the oil supply device further includes a third supply oil passagebranching from a portion located on a downstream side of the cooler inthe second supply oil passage and structured such that the oil passingthrough the cooler is supplied to the rotating electrical machine. 25.The oil supply device according to claim 12, wherein the first selectorvalve and the second selector valve are structured by a common spoolvalve having a common spool.
 26. The oil supply device according toclaim 13, wherein: the vehicular drive transmission device furtherincludes a rotating electrical machine provided in the power transferpath and configured to drive the wheel, and the oil supply devicefurther includes a third supply oil passage branching from a portionlocated on a downstream side of the cooler in the second supply oilpassage and structured such that the oil passing through the cooler issupplied to the rotating electrical machine.
 27. The oil supply deviceaccording to claim 13, wherein the first selector valve and the secondselector valve are structured by a common spool valve having a commonspool.
 28. The oil supply device according to claim 13, wherein thefirst selector valve, the second selector valve, and the third selectorvalve are structured by a common spool valve having a common spool. 29.The oil supply device according to claim 28, wherein: the common spoolvalve is configured to switch a first state and a second state dependingon a position of the spool, in the first state, the oil discharged fromthe first pump is cooled by the cooler and then supplied to thetransmission, and the oil discharged from the second pump is supplied tothe connection oil passage, and in the second state, the oil dischargedfrom the first pump is supplied to the transmission through the bypassoil passage, and the oil discharged from the second pump is cooled bythe cooler and then supplied to the friction engagement device.